Rotary valve



March 2 1943. w R TUCKER 2,312,941

ROTARY VALVE I Filed July 30, 1941 4 Sheets-Sheet 1 2 March 2 1943. w. R. TUCKER 2,312,941

ROTARY VALVE Filed July 30, 1941 4 Sheets-Sheet 2 March 1943. W, R TUCKER 2,312,941

ROTARY VALVE Filed July 30,' 1941 4 Sheets-Sheet 3 56 45- 67 F5- g 55 l,68

65 [7a z 63 52 -W f.

W. R. TUCKER ROTARY VALVE March 2 1943.

Filed July 30, 1941 4 Sheets-Sheet 4 Patented Mar. 2, 1943 ROTARY VALVE Warren R. Tucker, Dayton, hio, assignor to The Hydraulic Development Corporation, Inc., Wilmington, Del., a corporation oi' Delaware Application July 30, 1941, Serial No. 404,683

Claims.

This invention relates to valves and, in particular, to rotary valves.

With rotary valves heretofore known, diillculties have been encountered to move such valves when under high hydraulic pressure. The rea.- son therefor is believed to lie in the dimculty to make the rotor and the bore therefor perfectly parallel. In other words, it is practically impossible to provide exactly the same clearance all around the valve rotor so that, during the operation of the valve, uid is wedged in on one side of the valve rotor and squeezed out on the opposite side of said rotor with the result that the valve rotor assumes an eccentric position.

In cases where the valve rotor is subjected to one-sided pressure, the rotor is naturally pushed to one side and the situation described above is even worse. While the last mentioned diiiiculty has, at least in part, been remedied by the pro-- vision of a groove, or the like, around the rotor in an effort to equalize the uid pressure on opposite surfaces of the rotor, the drawback caused by the impossibility to make the rotor surface perfectly parallel to the surface of the valve boretherefor remained, and caused serious diiliculties in high pressure hydraulic systems, which made it necessary to use increased force for shifting the valves, and to make the valves relatively heavy in order to enable them to withstand the said increased force and wear.

Accordingly, it is an object of the invention to provide an improved rotary valve which will be operable without employing undue force, and thereby enable a lighter construction.

It is another object to provide a rotary valve which, even when under one-sided high pressure,

will allow of an easy shifting movement of the valve rotor.

A further object of the invention consists in the provision of a rotary valve in which the sealing or valving surfaces of the rotor are separated from the bearing surfaces of the rotor.

It is still another object of the invention to provide a rotary valve in which the position of the rotor axis with regard to the axis of the valve bore may be adjusted to vary the location of the rotor within the valve bore so as to equalize the clearance around the rotor as far as possible.

These and other objects and advantages of the invention will appear more clearly from the following specification in connection with the accompanying drawings, in which:

Figure 1 shows a section through a first embodiment of a rotary valve according to the invention.

Figure 2 is a section along the line 2-2 of Figure 1.

Figure 3 is a section along the line 3-3 of Figure 1.

Figure 4 illustrates in section a second embodiment of the invention, showing a rotary valve with a hydraulically unbalanced rotor.

Figure 5 shows a hydraulic press with an unbalanced valve.

Figures 6, 7 and 8 illustrate different positions of the unbalanced rotary'valve of Figure 5.

Figure 9 is a longitudinal section through the valve shown in Figures 5 to 8.

Figure 10 illustrates a perspective view of the rotor of Figure 9.

vFigure 11 is a section through a further embodiment of the invention.

Figure 12 is a section along the line I2-i2 of Figure 11.

Figure 13 is a section similar to that of Figure 12, but with the rotor in a different position.

Figure 14 is a perspective view of the rotor of Figure 1.

Figure 15 is a perspective view of the rotor of Figure 11.

Figure 16 shows actuating means for a valve according to the invention.

Figure 17 shows another embodiment of actuating means for a valve according to the inven tion.

Figure 18 is a section along the line lil- I8 of Figure 17. o

General arrangement The rotary member of the rotary valve according to the invention is, in ccntradistinction to the rotary valves heretofore known, not supported by the adjacent wall portion of the stationary valve member, but by accurate anti-friction bearings. In other words, with the valve according to the invention, the sealing or valving surfaces of the rotary valve member are separated from the bearing surfaces of the rotor, which bearing surfaces are supported by anti-friction bearings maintaining the sealing or valving surfaces of the rotary valve properly spaced from the adjacent wall portions of the stationary valve member.

According to a further embodiment of the invention, the anti-friction bearings are associated with adjusting means adapted to adjust the antifriction bearings, thereby varying the location of the rotary valve member relativevto the stationary valve member.

Structural arrangement ber 8 which is rotatable within the bore 9 of the stationary valve. casing I.

The shaft 1 is provided with an enlarged portion I mounted in the inner race II of a ball bearing I2, the outer race I3 of which is mounted in the bore 9 of the stationary valve casing I and engaged by an annular portion 3a of the end member 3. Similarly, the opposite end of the rotary valve member 8 is provided with a shaft lportion I4 mounted in the inner race I5 of the ball bearing I6, the outer race I1 of which is located in the bore 9 of the stationary casing I and engaged by an adjusting member I8 adapted to be pressed against the outer race I1 by means of screws I9 passing through the end member 2.

The stationary casing I comprises two oppositely located bores or ports 2li and 2i, which are in continuous communication with an annular groove 22 in the rotary valve member 8 and are provided with a thread for receiving hose or pipe connections. The stationary casing I furthermore comprises a threaded bore or port 23 and a further oppositely located threaded bore or port 24. Communicating with the annular groove 22 are two oppositely located channels 25 and 26 which are adapted to communicate with the ports 23 and 24 respectively when the rotary valve member 8 occupies the position shown in Figure 1.

Substantially rectangular to the ports 23 and- 24 are threaded ports 21 and 28 in the casing I which are adapted to be connected with each other by a bore 29, passing through the rotary valve member 8, when the rotary valve member occupies the position shown in Figures 1 and 2.

Passing through the rotary valve member 8, in longitudinal direction thereof, is a bore 30, one end of which leads into the space between the ball bearing I6 and the adjusting member I8, whereas the other end of the bore 30 communicates through a channel 3| with the space between the end member 3 and the ball bearing I 2. When the bore 30 and the bore 29, communieating therewith, are connected to an exhaust, the channel 3i serves to collect leakage passing past the ball bearing I2, whereas when the bore 30 is connected to the pressure side, the channel 3| will serve to equalize the pressure axially acting upon the rotary valve member 8.

The valve shown in Figure 1 constitutes a baalanced four-way valve which, in the position shown in Figure 1, establishes connection between the ports 20 and 23 on one hand, and the ports 2i and 24 on the other hand, whereas the port 21 communicates with the port 28 and, through bore 30, with the bore 5. If desired, one of the ports 20, 23 and one ofy the ports 2|, 24 may be plugged, the two extra ports merely being for convenience. When the rotary valve member 8 is rotated by 90 degrees, the bore 29 wilt establish communication between the ports 23 and 24, while the ports 21 and 28`will communicate, through channels 28 and 25 respectively, and groove 22, with the ports 20 and 2i.

The vital feature of the valve shown in Figures 1 to 3 is the suspension of the valve rotor in the close fitting anti-friction bearings I2 and I8. Because of this feature, the surge of fluid through the valve is prevented from forcing the rotor against one wall of the bore in the casing I, so that the rotor is maintained frictionally free. Since the rotary valve member 8 is hydraulically balanced, due to the provision of the annular groove 22, it is quite suilicient to provide ball bearings at the end of the rotary valve member 8 ior supporting and maintaining the rotary- Athe valve is preferably constructed in the manner shown in Figure 4.

'I'he valve of Figure 4 substantially corresponds to that of Figure 1 and similar parts have been designated with the same reference numerals, however, with the additional letter a. The valve of Figure 4, aside from being unbalanced, differs from the valve of Figure 1 primarily in that the rotary valve member 8a is supported at its shaft portions Illa and I4a by tapered roller bearings 32 and 33.

The inner race 34 of the roller bearing 32 is mounted on the shaft portion Illa, whereas the outer race 35 of the roller bearing 32 is mounted in the bore 36 and clamped against the annular shoulder 31 by means of the end member 3a. The inner race 38 of the tapered roller bearing 33 is mounted on the shaft portion I4a, whereas the outer race 39 of the bearing 33 is slidably mounted in the bore 40 of the casing la. The outer race 39 of the bearing 33 is engaged by an annular portion 4I of the end member 42 for adjusting the bearing 33, and the extent of adjustment is determined by the thickness of the shim or shims 43 interposed between the left end side of the casing la and the end member 42, connected to the casing by means of screws 44.

As will be clear from the drawings, the adjustment of the tapered roller bearing 33 also adjusts the tapered roller bearing 32 and, thereby, enables an adjustment of the rotary valve member 8a and its axis relative to the axis of the valve casing Ia so that the clearance between the sealing or valving surface of the rotary valve member 8a and the adjacent wall portion of the casing Ia may be equalized as far as possible. It will also be noted that the surface of the casing Ia engaged by the outer races 35 and 39 of the tapered roller bearings 32 and 33 is separated from the wall portion of the casing Ia cooperating with the adjacent surface of the rotary valve member 8a so that only a small portion of the casing is to be machined for a close fit of the tapered bearings 32, 33.

The tapered bearings 32 and 33 take up all radial forces exerted by the pressure fluid and tending to dislocate the axis of the rotary valve member with regard to the axis of the casing and prevent any such dislocation. Since, on the other hand, the rotary valve member 8a is journalled in tapered anti-friction bearings, the rotary valve member can easily be shifted in spite of the hydraulic forces exerting one-sided pressure on the rotary valve member 8a.

Another unbalanced valve is shown in Figure 9 which may be used in connection with thev press of Figure 5. The said press does not form a part of the present invention, and for a more b 9,819,941 detailed description thereof reference may be had to U. B. Patent application, Serial No. 330,888, tiled April 22, 1940. by Warren R. Tucker.

The valve of Figures 8 to 8 comprises a valve casing. 4l having rotatablymounted therein a rotary valve member 48, which latter has two half circular recesses 41 and 48 separated from each other by ribs 48 and 84X The rotary valve member 4I furthermore comprises an annular recess 8i which communicates through a channel 82 with the recess 41. The rotary valve member 48 has a longitudinal bore ll which communicates through' a passageway 84 with the recess 48;

Connected to the left side of the valve casina 48, by means of screws 88, isan end member 88 with a port 81 which. in Figures 5 to 8, is connected to the pressure side of the pump Il. The port B1 is in hydraulic communication with the bore 88 through an opening I8 provided in the adjust-i' tapered roller bearing et; the outer race 8B of which is also mounted in the bore 88 of the casing 8e. The outer race 8B is engaged by an annular portion 88 of the end member 81 connected to the casing 48 by screws 88. The valve casing 48 has four ports 89, 10, 1I and 12.

As will be seen from the drawings, the valve of Figure 9, in addition to being radially urbalanced, is also axially unbalanced. However, the tapered roller bearings 62 and 84 take up axial as well as radial thrusts and. thereby. prevent the pressure fluid in the valve from movingV the rotary valve member radially and axially with regard to the axis of the valve casing 4B. The rotary valve member remains, therefore, properly located and, at any time, can be shifted from one position into another position without requiring undue forces and exerting undue wear upon lthe rotary valve member and the valve casing.

The valve illustrated in Figure 1l constitutes a further yiriiinrovernent with regard to hydraulically balancing the rotary valve member. The valve of Figure l1 corresponds substantially to that of Figure 1, but differs therefrom by the provision of peripheral channels 18 and 14.

It has been found that the rotary valve member of Figures l and 3 becomes hydraulically unbalanced when the portv 24 is connected to a pressure line, while the ports 23 and 21 are plugged, and the rotary valve member is shifted from its Figure 2 position into neutral position, i. e., into a position where the bore 29 occupies a. position intermediate the ports 24 and 28. The reason therefor is that, although at the time of said shifting operation the fluid pressure in the port 24 equals the' pressure of the fluid entrapped between the now shifted rotary valve member and the port 23, fluid leaks out from the port 23, thereby causing a decrease in pressure of the pressure fluid entrapped in the port 28. Consequently, the pressure in port 24, which as. mentioned is connected to a pressure line,

tends to axially offset the rotary valve member,

and would actually do so if it were not for the anti-friction bearings provided according to the invention for supporting the rotary valve member.

However, since the elimination of this onesided pressure on the rotary valve member, 'in neutral position of the latter, will make it poslili by even lighter anti-friction bearings, the rotary valve member has, according to Figure 11, been provided with peripheral slots or channels 18, 14 being, on one end thereof, in with`an annular groove".

Referring now to Figures 12 and 13 in which the ports 28 and 21 are closed toward-the outside by plugs 18 and 11, and assuming that the rotary valve membe'r has been shifted from Figure 12 position to Figure 13 position, it will be noted that the channels 18 and 14 are so located that they communicate with the ports 28 and 24. Consequently, fluid pressure-is continuously conveyed from the port 24, which is assumed to be connected with a pressure line. to port 28 through channel 13, groove 18 and channel 14. Thereforafthe pressure in ports 28 and 24'is equalized and,no matter how long the Valve will be held in Figure 13 position, will stay equalized, thereby maintaining the ro- -tary valve member hydraulically balanced.

Since, thus, the rotary valve member is at any and in all possible conditions, to assure a proper and easy operation of the rotary valve member.

The rotary valve member of the various ernbodiments shown in the drawings may be operated manually by a handle keyed or otherwise connected thereto, but, if desired, also mechanical or fluid operating mechanisms may be provided. For instance, according to Figure 16, the shaft 18 of the rotary valve member has keyed thereto an arm with a slot 8i in which is slidably movable a pin 82 connected to a plunger 83 reciprocably mounted in a cylinder 84.

The cylinder 84 has connected thereto two pipe lines and 88 which are connected by means of a two-way valve (not shown) with a fiuid pressure source so that the plunger 83 may selectively be moved in one or the. other direction, thereby shifting the valve shaft 19 accordingly.

According to the embodiment of Figure 17, which is intended for actuation of a valve to be rotated in one direction only as, for instance, the valve shown in Figures 6 to 9, the shaft 81 of the rotary valve member is connected with a stall motor 88. Keyed to the shaft 81 is a disc 88 with a plurality of-notches 80 corresponding in number to the possible different positions of the valve. The notches 98 are adapted sequentially to be engaged by a tongue or stop member 8i whichis continuously urged by a. spring 92 into engagement with the disc 89 and is adapted to be withdrawn therefrom by energization of the solenoid 98.

While the valve according to the invention has been shown in the drawings with a stationary casing housing the rotary valve member, it is, of course, understood that also the reverse arrangement may be adapted in which the casing I is rotatable while the valve shaft or valve member is stationary.

. It will be understood that I desire to compre'- Y 1. A rotary valve comprising in combination a stationary valve member having at least threesible to properly support the rotary valve member communication ports therein, a rotatable valve member with a plurality ot passages for cooperation with said ports, said passages being so arranged as to hydraulically balance said rotatable valve member against thrust due to pressures in two of said ports in all positions of the rotatable valve member, and additional passages arranged to balance the valve member against thrust due to pressure in a third one oi' said ports when out of communication with the others of said ports.

2. A rotary valve comprising in combination a stationary valve member having at least three ports therein, a rotatable valve lmember `with a plurality of passages for cooperation with said ports, said passages being so arranged as to hydraulically balance said rotatable valve member against thrust due to pressures in two of said ports in all positions of the rotatable valve member, anti-friction bearings interposed between said stationary and said rotatable valve member for supporting the latter, and additional passages arranged to balance the valve member against thrust due to pressure in a third one of said ports when out of communication with the others of said ports.

3.l A rotatable valve comprising in combination a stationary valve member having a plurality of ports therein including supply, exhaust and one to pressure in one service port when said service port is out o! communication with the others of saidA ports. v

4. A. rotatable valve comprising in combination a stationary valve member having a plurality of ports therein including supply. exhaust and one or more service-ports, a rotatable valve member with a pluralityof passages for cooperation with said ports. said passages being so arranged as to hydraulically balance said rotatable valve member against thrust due to pressures in said supply and exhaust ports in all positions of the valve member, anti-friction bearings interposed between said stationary and said rotatable valve member for supporting the latter, and additional passage means arranged to balance the valve member against thrust due to pressure in one service port when said service port is out of communication with the others of said ports.

5. A rotatable valve comprising in combination a stationary valve member having a plurality of ports therein including supply, exhaust and one or more service ports, a rotatable valve member with a plurality of passages for cooperation with said ports, said passages being so arranged as to f hydraulically balance said rotatable valve member against thrust due to pressures in said supply and exhaust ports in all'positions of the valve member, anti-friction'roller bearings interposed between said stationary and said rotatable valve member for supporting the latter, and additional passage means arranged to balance the valve member against thrust due to pressure in one service port when said service port is out of communication with the others of said ports.

WARREN R. TUCKER. 

